Countershaft

ABSTRACT

A countershaft as disclosed herein may include one or more bearing zones along its axial length. Each bearing zone may include one or more radial holes in fluid communication with one or more grooves, respectively, and one or more axial channels formed along the longitudinal length of the countershaft. Each groove may be positioned adjacent an interface between a rotating member and a non-rotating member and include one or more features therein, such as a profile and/or taper.

CROSS REFERENCE TO RELATED APPLICATIONS

This patent application claims priority from provisional U.S. Pat. App.Nos. 61/775,584 and 61/775,572 both filed on Mar. 9, 2013, and thispatent application also claims priority from and is acontinuation-in-part of U.S. patent application Ser. No. 14/203,556filed on Mar. 10, 2014, which applications are incorporated by referenceherein in their entireties.

FIELD OF INVENTION

The present invention relates to interfaces between a rotatable andnon-rotatable member.

STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT

No federal funds were used to develop or create the invention disclosedand described in the patent application.

REFERENCE TO SEQUENCE LISTING, A TABLE, OR A COMPUTER PROGRAM LISTINGCOMPACT DISK APPENDIX

Not Applicable

BACKGROUND

Journal bearings may have one or more inlets and/or grooves/features inthe bore. Generally, the configuration and number of features affectboth the static and dynamic performance of the bearing. Compared to astandard cylindrical bore bearing, profiled journal bearings, examplesof which include but are not limited to elliptical, multi-lobe taperland, and offset bore bearings may be more stable due to lobes/featuresin the bore of the bearing. However, because such a bearing is a fixedprofile bearing, its performance (e.g., film thickness, maximum bearingtemperature, and stability) is typically optimized for one or just a fewloading conditions. Accordingly, when the load changes (e.g., direction,magnitude, etc.) it is common for the bearing performance to degrade.Furthermore, a profiled journal bearing may also exhibit instabilitieslike a standard cylindrical bore bearing under certain operatingconditions.

Examples of journal bearings are shown in U.S. Pat. Nos. 6,966,700;6,547,438; 5,480,234 and 4,097,094 and U.S. patent application Ser. No.12/708,439, all of which are incorporated by reference herein in theirentireties.

BRIEF DESCRIPTION OF THE FIGURES

In order that the advantages of the invention will be readilyunderstood, a more particular description of the invention brieflydescribed above will be rendered by reference to specific embodimentsillustrated in the appended drawings. Understanding that these drawingsdepict only typical embodiments of the invention and are not thereforeto be considered limited of its scope, the invention will be describedand explained with additional specificity and detail through the use ofthe accompanying drawings.

FIG. 1 provides a perspective view of a multi-lobe taper land borebearing as found in the prior art.

FIG. 2A provides a perspective view of a first illustrative embodimentof a bearing with axial variations.

FIG. 2B provides an axial end view of the embodiment shown in FIG. 2A

FIG. 2C provides an axial cross-sectional view of the embodiment shownin FIGS. 2A and 2B along line J-J from FIG. 2B.

FIG. 2D provides a radial cross-sectional view of the embodiment shownin FIGS. 2A-2C along line K-K from FIG. 2C.

FIG. 2E provides an axial cross-sectional view of the embodiment shownin FIGS. 2A-2D along line L-L from FIG. 2D.

FIG. 3A provides a perspective view of a second illustrative embodimentof a bearing with axial variations.

FIG. 3B provides an axial end view of the embodiment shown in FIG. 3A

FIG. 3C provides an axial cross-sectional view of the embodiment shownin FIGS. 3A and 3B along line J-J from FIG. 3B.

FIG. 3D provides a radial cross-sectional view of the embodiment shownin FIGS. 3A-3C along line K-K from FIG. 3C.

FIG. 3E provides an axial cross-sectional view of the embodiment shownin FIGS. 3A-3D along line L-L from FIG. 3D.

FIG. 4A provides a perspective view of a third illustrative embodimentof a bearing with axial variations.

FIG. 4B provides an axial end view of the embodiment shown in FIG. 4A

FIG. 4C provides an axial cross-sectional view of the embodiment shownin FIGS. 4A and 4B along line J-J from FIG. 4B.

FIG. 4D provides a radial cross-sectional view of the embodiment shownin FIGS. 4A-4C along line K-K from FIG. 4C.

FIG. 4E provides an axial cross-sectional view of the embodiment shownin FIGS. 4A-4D along line L-L from FIG. 4D.

FIG. 5A provides a perspective view of a fourth illustrative embodimentof a bearing with axial variations, wherein the axial variations are onthe outside diameter.

FIG. 5B provides a detailed side view of a portion of the embodimentshown in FIG. 5A.

FIG. 5C provides an axial end view of the embodiment shown in FIGS. 5A &5B.

FIG. 5D provides a radial cross-sectional view of the embodiment shownin FIGS. 5A & 5B along line J-J from FIG. 5B.

FIG. 6A provides a perspective view of a fifth illustrative embodimentof a bearing with axial variations, wherein the axial variations are onthe outside diameter.

FIG. 6B provides a detailed side view of a portion of the embodimentshown in FIG. 6A.

FIG. 6C provides a radial cross-sectional view of the embodiment shownin FIG. 6B along line C-C.

FIG. 6D provides a radial cross-sectional view of the embodiment shownin FIG. 6B along line B-B.

FIG. 6E provides side view of a portion of an embodiment similar to thatshown in FIG. 6A, wherein the grooves are configured differently.

FIG. 7A provides a perspective view of a sixth illustrative embodimentof a bearing with axial variations, wherein the axial variations are onthe outside diameter.

FIG. 7B provides a detailed side view of a portion of the embodimentshown in FIG. 7A.

FIG. 7C provides a radial cross-sectional view of the embodiment shownin FIG. 7B along line C-C.

FIG. 7D provides a radial cross-sectional view of the embodiment shownin FIG. 7B along line B-B.

FIG. 8A provides a side view of a first illustrative embodiment of acountershaft.

FIG. 8B provides an end view of the embodiment of a shaft with axialvariations shown in FIG. 8A.

FIG. 8C provides an axial cross-sectional view the embodiment of a shaftwith axial variations shown in FIGS. 8A & 8B along line A-A from FIG.8B.

FIG. 8D provides a radial cross-sectional view of the embodiment of ashaft with axial variations shown in FIGS. 8A-8C along the line C-C fromFIG. 8C.

FIG. 8E provides a radial cross-sectional view of the embodiment of ashaft with axial variations shown in FIGS. 8A-8D along the line B-B fromFIG. 8C.

FIG. 9A provides a side view of a second illustrative embodiment of ashaft with axial variations.

FIG. 9B provides a detailed view of one portion of the embodiment of ashaft with axial variations shown in FIG. 9A.

FIG. 9C provides a radial cross-sectional view of the embodiment of ashaft with axial variations shown in FIGS. 9A & 9B along the line B-Bfrom FIG. 9A.

DETAILED DESCRIPTION—LISTING OF ELEMENTS

ELEMENT DESCRIPTION ELEMENT # Prior art bearing 4 Lobe 6 Shaft 8 Bearingwith axial variations 10 Bore 12 Axial channel 14 Notch 15 Bearingsurface 16 Spacer 17 Main body 18 First zone 20 Radial hole 22 Groove 24Taper 26 Second zone 30 Radial hole 32 Groove 34 Taper 36 Third zone 40Radial hole 42 Groove 44 Taper 46 Countershaft 100 Spacer 112 Axialchannel 114 Land 116 First bearing zone 120 Radial hole 122 Groove 124Taper 126 Second bearing zone 130 Radial hole 132 Groove 134 Taper 136

DETAILED DESCRIPTION

Before the various embodiments of the present invention are explained indetail, it is to be understood that the invention is not limited in itsapplication to the details of construction and the arrangements ofcomponents set forth in the following description or illustrated in thedrawings. The invention is capable of other embodiments and of beingpracticed or of being carried out in various ways. Also, it is to beunderstood that phraseology and terminology used herein with referenceto device or element orientation (such as, for example, terms like“front”, “back”, “up”, “down”, “top”, “bottom”, and the like) are onlyused to simplify description of the present invention, and do not aloneindicate or imply that the device or element referred to must have aparticular orientation. In addition, terms such as “first”, “second”,and “third” are used herein and in the appended claims for purposes ofdescription and are not intended to indicate or imply relativeimportance or significance.

Referring now to the drawings, wherein like reference numerals designateidentical or corresponding parts throughout the several views, FIG. 1provides an axial view of a prior art bearing 4 having three lobes 6,consisting of the bearing surface between oil feed grooves or holes,equally spaced about the bore 12 formed in the main body 18 of the priorart bearing 4.

Such a design may be plagued by various problems, including but notlimited to those described in detail above.

A first illustrative embodiment of a bearing with axial variations 10 isshown in perspective in FIG. 2A. This embodiment may be designed toaccommodate different shaft 8 diameters such that the diameter of thebore 12 formed in the main body 18 may be slightly larger than theoutside diameter of the shaft 8. For example, in one embodiment thediameter of the bore 12 may be 3.509 inches, outside diameter of themain body 18 may be 5.600 inches, and the axial length of the main body18 may be 3.500 inches such that the bearing with axial variations mayaccommodate a shaft 8 having a diameter of 3.5 inches. However, thespecific dimensions of the bearing with axial variations 10 of featuresthereof in no way limit the scope thereof as disclosed and claimedherein, and the bearing with axial variations 10 extends to thosedesigned to accommodate a shaft 8 of any diameter and any bearing withaxial variation 10 having any outside diameter or axial length.

The bearing with axial variations 10 may include a main body 18 that maybe configured as a two-piece design, wherein each piece of the main body18 approximately constitutes one-half of the main body 18.Alternatively, the main body 18 may be formed as one integral member asshown for the embodiments pictured herein. Additionally, still otherembodiments exist in which the bearing with axial variations 10 isformed from more than two pieces engaged with one another. It iscontemplated that a bearing with axial variations 10 will achieve betterperformance (e.g., more stability, acceptable temperatures, etc.) for awider range of performance requirements than that of prior art bearings4, which requirements may be predetermined based on variable loads.Accordingly, it is contemplated that compared to the prior art, thebearing with axial variations 10 may increase the resistance tohalf-speed whirl while retaining similar load capacity, allowing thebearing/rotor system to operate at higher speeds or lighter shaftweights; increase film thickness at non-design points; decrease maximumbearing temperature at non-design points; and provide a higher safetymargin.

The performance of a bearing with axial variations 10 may be increasedcompared to a prior art bearing 4 by configuring the bore 12 withadditional features at different positions along the axial dimension ofthe bore 12. For example, the embodiment shown in FIG. 2A may include afirst zone 20 configured with one or more radial holes 22 extending fromthe exterior surface of the bearing housing 18 through the bore 12. Itis contemplated that lubricant may be supplied to features in the bore12 via a lubricant supply source (not shown), such as a supply ofpressurized lubricant. However, the specific method and/or apparatusused to supply lubricant to any radial hole 22, 32, 42 of any embodimentof the bearing with axial variations 10 in no way limits the scope ofthe present disclosure. As shown, the first zone 20 (which may bedefined as the zone positioned to the right of FIG. 2C) may includethree radial holes 22 equally spaced about the bore 12 (i.e., at 120degrees from one another), which radial holes 22 may be configured to bein fluid communication with respective grooves 24 configured in the bore12.

Each groove 24 and/or land 16 may be configured with a specific profile,geometry, and/or features therein (e.g., grooves, voids, pits, channels,tapers 26, axial notches, etc.) to cooperate with and/or optimize one ormore lands 16 that may be configured on the bore 12. The specificprofile, geometry, and/or features of any groove 24, 34, 44 and/or land16 of any zone 20, 30, 40 in no way limits the scope of the bearing withaxial variations 10 as disclosed and claimed herein. For example, one ormore grooves 24, 34, 44 in an embodiment of a bearing with axialvariation 10 may be configured as a lemon bore, with or without a taper26, etc. without limitation. Generally, and without limitation, thespecific configuration of the taper 26, 36, 46 (if present) will dependat least on the direction of relative rotation between the bearing withaxial variations 10 and the shaft 8 or other structure that the bearingwith axial variations 10 rotates with respect to. In another embodiment,the land 16 may be configured such that the cross-sectional shapethereof is generally semi-circular. Additionally, any radial hole 24,34, 44 may have an infinite number of configurations (e.g., different orvarying cross-sectional shapes along the length thereof, a largerdiameter portion with a step to a smaller diameter portion (as shown inthe first and second embodiments of a bearing with axial variations 10),etc.), and the specific configuration of any radial hole 24, 34, 44 inno way limits the scope of the present disclosure. Furthermore, thenumber of radial holes 22, 32, 42 in a given zone 20, 30, 40 need not beequal to the number of grooves 24, 34, 44 and/or tapers 26, 36, 46 in agiven zone 20, 30, 40. The number of tapers 26, 36, 46 need not be equalto the number of grooves 24, 34, 44 in a given zone 20, 30, 40. That is,a first groove 24 in the first zone 20 may include a taper 26, but asecond groove 24 therein may not. And the first groove 24 may be influid communication with a first radial hole 22, but the second groove24 may not be associated with any radial hole 22.

The first embodiment of a bearing with axial variations 10 may alsoinclude a second zone 30, which may be similarly configured to the firstzone 20 such that three radial holes 32 may be equally spaced about thebore 12 in the second zone 30. The radial holes 32 may be configured tobe in fluid communication with a respective groove 34 configured in thebore 12. It is contemplated that the first zone 20 may be offsetrotationally with respect to the second zone 30, which is best shown inFIG. 2B. This offset will vary from one embodiment of the bearing withaxial variations 10 to the next, and in some bearings with axialvariation 10 there will be no offset between zones 20, 30, but insteadhave differences in the features of the grooves 24, 34 formed in therespective zones 20, 30. In the first illustrative embodiment, thesecond zone 30 may be offset from the first zone 20 by approximately 40degrees, but the specific offset from one zone 20, 30, 40 to the next inno way limits the scope of the present disclosure.

The first embodiment of a bearing with axial variations 10 may alsoinclude a third zone 40, which may be similarly configured to the firstand second zones 20, 30 such that three radial holes 42 may be equallyspaced about the bore 12 in the third zone 40. The radial holes 42 maybe configured to be in fluid communication with a respective groove 44configured in the bore 12. It is contemplated that the third zone 40 maybe offset rotationally with respect to the second zone 30, which is bestshown in FIGS. 2B & 2C. This offset will vary from one embodiment of thebearing with axial variations 10 to the next, and in some bearings withaxial variation 10 there will be no offset between zones 30, 40 butinstead have differences in the features of the grooves 34, 44 formed inthe respective zones 30, 40. Additionally, in the illustrativeembodiment shown in FIGS. 2A-2E, the first zone 20 may be at the samerotational position as the third zone 40, such that the offsettherebetween is zero. In other embodiments of the bearing with axialvariations 10, the first zone 20 may be offset with respect to thesecond zone 32 without limitation. Furthermore, the third zone 40 may beoffset from both the first zone 20 and the second zone 30. Otherembodiments of the bearing with axial variation 10 may include more thanthree zones 20, 30, 40, and still other embodiments include only twozones 20, 30. Accordingly, the number of zones 20, 30, 40 and/or theirrelative rotational offset with respect to one another in no way limitsthe scope of the present disclosure. Additionally, the axial offsetbetween zones 20, 30, 40 may be of any length or of no length withoutlimitation. That is, in some embodiments the axial offset of zones 20,30, 40 may be zero, while in other embodiments the axial offset betweenzones 20, 30, 40 may be of a specific, predetermined length greater thanzero. Accordingly, the number of zones 20, 30, 40 and/or their relativeaxial offset with respect to one another in no way limits the scope ofthe present disclosure.

A second embodiment of a bearing with axial variations 10 is shown inFIGS. 3A-3F. As with the embodiment shown in FIGS. 2A-2E, thisembodiment may include three zones 20, 30, 40, which is in no waylimiting to the scope of the bearing with axial variations 10. Thesecond illustrative embodiment is similar to the first illustrativeembodiment except for the configuration of the first and third zones 20,40 and the relative rotational offset between zones 20, 30, 40. In thesecond illustrative embodiment, the first and third zones 20, 40 may beformed with two radial holes 22, 42 opposed to one another such thatthey are separated by 180 degrees within their respective zones 20, 40,which is best shown in FIG. 3B. Again, the first and third zones 20, 40may be rotationally aligned with one another. In the second illustrativeembodiment, the first and third zones 20, 40, may be rotationally offsetwith respect to the second zone 30 by 15 degrees. However, as previouslystated, the number of zones 20, 30, 40 and/or their relative rotationaloffset with respect to one another in no way limits the scope of thepresent disclosure.

A perspective view of third illustrative embodiment of a bearing withaxial variations 10 is shown in FIG. 4A. This embodiment may include twozones 20, 30, having offset radial holes 22, 32, respectively, leadingto grooves 24, 34 formed in the bore 12. Again, the rotational offset ofthe various zones 20, 30 may vary from one specific embodiment to thenext, but may be approximately 40 degrees as pictured for the thirdillustrative embodiment of a bearing with axial variations 10.

Each radial hole 22, 32, 42 may intersect a groove 24, 34, 44 at adifferent position of the groove 24, 34, 44. For example, in the firstand second illustrative embodiments, the radial holes 22, 32, 42 mayintersect the respective grooves 24, 34, 44 approximately at thecenterline of the groove 24, 34, 44 with respect to the axial dimension.However, in the third embodiment, the radial holes 22, 32 may intersectthe respective grooves 24, 34 at an extreme end of the groove 24, 34with respect to the axial dimension. As previously stated, the specificconfiguration of any grooves 24, 34, 44 and/or lands 16 in the bearingwith axial variations 10 in no way limits the scope of the presentdisclosure. Accordingly, the bearing, with axial variations 10 extendsto any groove 24, 34, 44 and/or land 16 configuration, including but notlimited to variations in the axial position at which a radial hole 22,32, 42 intersects a respective groove 24, 34, 44.

It is contemplated that a bearing with axial variations 10 with threezones 20, 30, 40 may be less likely than a bearing with axial variations10 with two zones 20, 30 to misalign because three zones 20, 30, 40(wherein the first and third zones 20, 40 may be rotationally aligned)may be more likely to have an equal axial pressure balance throughout.However, other embodiments of the bearing with axial variations 10 mayinclude additional zones 20, 30, 40, such as fourth and fifth zones,etc. without limitation.

A fourth illustrative embodiment of a bearing with axial variations isshown in FIGS. 5A-5D. In this embodiment, the various grooves 24, 34,44, land(s) 16, and/or features of the bearing with axial variations 10may be configured on the outside diameter of the bearing with axialvariation 10. Such an embodiment of the bearing with axial variation 10may be configured such that it may rotate relative to a main body, andthe main body may be formed with a bore therein to accommodate thebearing with axial variations 10. In such a configuration, the main bodymay rotate and the bearing with axial variations 10 may be stationary,or vice versa. Alternatively, both the bearing with axial variations 10and the main body 18 may rotate, albeit at different rates. Accordingly,the configuration of stationary and/or rotating components in no wayaffects the scope of the bearing with axial variations 10 as disclosedand claimed herein.

As mentioned, a main body may be configured with a bore into which thebearing with axial variation 10 may be positioned. This embodiment maybe configured such that the radial cross-sectional shape of the bore isgenerally circular, although it may or may not be concentric with acenterline of the main body. The cross-sectional shape of the embodimentof a bearing with axial variations 10 shown in FIGS. 5A 5D, also may begenerally circular in shape. However, other embodiments may havedifferent radial and/or axial cross-sectional shapes without limitation,which may correspond to different cross-sectional shapes of a boreand/or main body having a bore formed therein. In the embodimentpictured in FIGS. 5A-5D, the axial variations may be configured on theoutside diameter, rather than on the bore 12 as described for theprevious embodiments. A perspective view of the fourth embodiment isshown in FIG. 5A. This embodiment may include three zones 20, 30, 40,and one or more grooves 24, 34, 44 may be configured in each zone 20,30, 40, respectively. However, as with the previous embodimentsdescribed above, other embodiments with features on the outside diametermay include additional zones 20, 30, 40, such as fourth and fifth zones,etc., and/or additional features in each groove 24, 34, 44, and/or land16 (such as tapers 26, 36, 46, notches, etc.) without limitation.

As shown in FIGS. 5A & 5B, a land 16 may be located adjacent a groove24, 34, 44 and/or integrated therewith. The area opposite the land 16adjacent a groove 24, 34, 44 may have any configuration suitable for theparticular application of the bearing with axial variations 10. Forexample, that area may be configured with a taper 26, 36, 46 or it mayhave a different profile and/or features therein. Alternatively, thatarea may not be configured with a profile therein and simply beconfigured as a smooth arc. A specific configuration is shown in FIG.5B, wherein the groove 24 may have a specific taper 26 and undercut.Other embodiments may have different configurations of grooves 24, 34,44 with or without a taper 26, 36, 46 and/or other profiles or featuresformed therein without limitation.

As shown in FIGS. 5C & 5D, an axial channel 14 may be configured on theinterior of the bearing with axial variations 10 along the longitudinalaxis thereof. The axial channel 14 may be in fluid communication withone or more radial holes 22, 32, 42. It is contemplated that lubricantmay be supplied to one or more radial holes 22, 32, 42 via a lubricantsupply source (not shown), such as a supply of pressurized lubricant.However, the specific method and/or apparatus used to supply lubricantto any radial hole 22, 32, 42 of any embodiment of the bearing withaxial variations 10 in no way limits the scope of the presentdisclosure. In the fourth embodiment, the first, second, and third zones20, 30, 40 may be configured with two radial holes 22, 32, 42 opposed toone another at 180 degrees, wherein the radial holes 22, 32, 42 may bein fluid communication with two respective grooves 24, 34, 44 in therespective zones 20, 30, 40. The radial holes 32 in the second zone 30may be rotationally offset from those in the first and/or third zones20, 40 by approximately 40 degrees. However, as previously describedabove for other embodiments of the bearing with axial variations 10, theorientation and/or number of zones 20, 30, 40; radial holes 22, 32, 42;grooves 24, 34, 44 and/or lands 16 in any of the zones 20, 30, 40 are inno way limiting.

A fifth illustrative embodiment of a bearing with axial variations isshown in FIGS. 6A-6E. This embodiment may be configured similarly tothat shown in FIGS. 5A-5D wherein the loves 24, 34 and land(s) 16 arepositioned on the outside diameter of the bearing with axial variation10. Accordingly, the fifth illustrative embodiment may be configuredsuch that the radial cross-sectional shape thereof is generallycircular, although it may or may not be concentric with the centerlineof a main body configured to accept the bearing with axial variations10. Other embodiments may have different radial cross-sectional shapeswithout limitation. A perspective view of the fifth embodiment is shownin FIG. 6A. This embodiment may include two or more zones 20, 30 and oneor more grooves 24, 34 may be configured in each zone 20, 30,respectively. In this embodiment, the first and second zones 20, 30 maybe rotationally offset with respect to one another. However, aspreviously described above for other embodiments of the bearing withaxial variations 10, the orientation and/or number of zones 20, 30;radial holes 22, 32; grooves 24, 34 and/or lands 16 in any of the zones20, 30, 40 are in no way limiting. The axial offset between features inany given zone 20, 30, 40 and/or between the zones 20, 30, 40 themselvesmay be of any length, including zero (as shown for the axial offset inthe embodiment pictured in FIG. 4C) without limiting the scope of thepresent disclosure, as described in detail above.

As shown in FIG. 6B, a land 16 may be located adjacent a groove 24, 34on either side thereof. Alternatively, on one or both areas adjacent agroove 24, 34 there may be a different configuration suitable for theparticular application of the bearing with axial variations 10. Forexample, that area may be tapered or have a different profile.Alternatively, that area may be formed without a profile therein. Thegrooves 24, 34 for the embodiment shown in FIGS. 6A-6D may have thespecific configuration is shown in FIG. 5C, wherein the groove 24 mayhave a specific taper 26 and undercut. Other embodiments may havedifferent configurations of grooves 24, 34 with or without a taper 26,36 or other profile and/or features formed therein without limitation. Adifferent configuration for the grooves 24, 34 is shown in theembodiment pictured in FIG. 6E, wherein the grooves 24, 34 may include aspecifically configured profile and/or taper 26, 36, therein.Additionally, the embodiment pictured in FIG. 6E may include a notch 15positioned adjacent one or more sides of each groove 24, 34 to provide apathway for lubricant.

As shown in FIGS. 6C & 6D, an axial channel 14 may be configured on theinterior of the bearing with axial variations 10, which axial channel 14may be in fluid communication with one or more radial holes 22, 32.Referring specifically to FIG. 6D, in the fifth embodiment, the firstzone 20 may be configured with three radial holes 22 spaced from oneanother by 120 degrees, wherein the radial holes 22 may be in fluidcommunication with three respective grooves 24. However, as previouslydescribed above for other embodiments of the bearing with axialvariations 10, the orientation and/or number of zones 20, 30, 40; radialholes 22, 32, 42; grooves 24, 34, 44 and/or lands 16 in any of the zones20, 30, 40 are in no way limiting.

As shown in FIG. 6C, the axial channel 14 may be configured such thatthe axial channel 14 may be in fluid communication with two radial holes32 formed in the second zone 30. In the fifth embodiment, the secondzone 30 may be configured with two radial holes 32 spaced from oneanother by 180 degrees, wherein the radial holes 32 may be in fluidcommunication with two respective grooves 34 formed in the second zone30. The radial holes 32 in the second zone 30 may be rotationally offsetfrom those in the first zone 20. In the embodiment shown in FIGS. 6A-6Ethe first zone 20 may be radially offset from the second zone 30 byapproximately 15 degrees. However, as previously described above forother embodiments of the bearing with axial variations 10, theorientation and/or number of zones 20, 30, 40; radial holes 22, 32, 42;grooves 24, 34, 44 and/or lands 16 in any of the zones 20, 30, 40 are inno way limiting.

A variation of the grooves 24, 34 is shown in FIG. 6E. In thisembodiment of a groove 24, 34, each groove 24, 34 may include a notch 15formed in one or more axial ends thereof. The notch 15 may provide apathway for lubricant to exit the groove 24, 34 upon specific,predetermined conditions. The radial holes 22, 32 for the bearing withaxial variations 10 shown in FIG. 6E may have any configurationdisclosed herein without limitation. Additionally, notches 15 may beincluded in any of the grooves 24, 34, 44 and/or lands 16 of anyembodiments disclosed herein without limitation.

A sixth illustrative embodiment of a bearing with axial variations isshown in FIGS. 7A-7E. A perspective view of the sixth embodiment isshown in FIG. 7A. This embodiment may be formed as two discrete bearingswith axial variations 10 separated by a spacer 17. The two bearings withaxial variations 10 may be integrally formed with one another and/or thespacer 17, or the bearings with axial variations 10 and/or spacer 17 maybe separately formed and later engaged with one another. For brevity,illustrative features of one of the bearings with axial variations 10will be described in detail, with the understanding that those featuresmay be applied to the other bearing with axial variations 10 oppositethe spacer 17. Furthermore, although the embodiment shown in FIGS. 7A-7Eincludes two discrete bearings 10, in other embodiments additionalbearings with axial variations 10 and/or spacers 17 may be includedwithout limitation.

This embodiment may be configured similarly to the embodiments shown inFIGS. 5A-6E wherein the land(s) 16 is positioned on the outside diameterof the bearing with axial variation 10. Accordingly, the sixthillustrative embodiment may be configured such that the radialcross-sectional shape thereof is circular, although it may or may not beconcentric with the centerline of a bore termed in the main body. Otherembodiments may have different radial cross-sectional shapes withoutlimitation.

Each bearing with axial variations 10 may include two or more zones 20,30, 40 and one or more grooves 24, 34, 44, and/or lands 16 may beconfigured in each zone 20, 30, 40, respectively. However, as previouslydescribed above for other embodiments of the bearing with axialvariations 10, those having one or more bearings with axial variations10 positioned adjacent one another (with or without a spacer 17positioned therebetween), the orientation and/or number of zones 20, 30,40; radial holes 22, 32, 42; grooves 24, 34, 44 and/or lands 16 in anyof the zones 20, 30, 40 are in no way limiting.

As shown in FIG. 7B, a land 16 and/or a taper 36, 46 may be locatedadjacent a groove 24, 34, 44 on either side thereof. Generally, andwithout limitation, the specific configuration of the taper 26, 36, 46(if present) will depend at least on the direction of relative rotationbetween the bearing with axial variations 10 and the main body or otherstructure that the bearing with axial variations 10 rotates with respectto. Alternatively, on one or both areas adjacent a groove 24, 34, 44there may be a different configuration suitable for the particularapplication of the bearing with axial variations 10. For example, one ormore areas adjacent a groove 24, 34, 44 may include a taper 26, 36, 46and/or or notch 15 thereon, or have a different profile. Alternatively,that area may be formed without a profile therein, such as theembodiment pictured in FIG. 6A. The grooves 24, 34, 44 for theembodiment shown in FIGS. 7A-7D may have the specific configuration isshown in FIGS. 7C & 7D, wherein the grooves 24, 34, 44 may be formedwith a specific taper 26, 36, 46 and undercut. Other embodiments mayhave different configurations of grooves 24, 34, 44 and/or lands 16 withor without a taper 26, 36, 46 or other profile formed therein withoutlimitation.

As shown in FIGS. 7C and 7D, an axial channel 14 may be configured onthe interior of the bearing with axial variations 10, which axialchannel 14 may be in fluid communication with one or more radial holes22, 32, 42 formed in the respective zones 20, 30, 40. In the sixthembodiment, the first, second, and third zones 20, 30, 40 may beconfigured with three radial holes 22, 32, 42 spaced from adjacentradial holes 22, 32, 42 in the same zone 20, 30, 40 by 120 degrees. Eachradial hole 22, 32, 42 may be in fluid communication with threerespective grooves 24, 34, 44 formed in the respective zones 20, 30, 40.The first and third zones 20, 40 may be rotationally offset from thesecond zone 30 by approximately 60 degrees. However, as previouslydescribed above for other embodiments of the bearing with axialvariations 10, the orientation and/or number of zones 20, 30, 40; radialholes 22, 32, 42; grooves 24, 34, 44 and/or lands 16 in any of the zones20, 30, 40 are in no way limiting.

The number, configuration, dimensions, geometries, and/or relativelocations of the zones 20, 30, 40; radial holes 22, 32, 42; grooves 24,34, 44; notches 15, and/or lands 16 will vary from one embodiment of thebearing with axial variations 10 to the next, as will the optimalconfiguration thereof. Accordingly, the bearing with axial variations 10as disclosed and claimed herein is in no way limited by the specificconstraints of those elements. In addition to optimizing the rotationaloffset between zones 20, 30, 40, the number of features (e.g., radialholes 22, 32, 42; grooves 24, 34, 44; grooves, tapers, profiles; etc.)grooves 24, 34, 44; and/or lands 16 and the configuration thereof may beoptimized for specific operational requirements and/or constraints.

The bearing with axial variations 10 and/or concepts thereof asdisclosed and claimed herein may extend to any bearing with a fixedprofile, including but not limited to plain cylindrical bore bearings,elliptical bore bearings, taper land bore bearings, pressure dam borebearings, tilting pad journal bearing, and offset half bearings.Furthermore, the present disclosure may be applied to counter shaft orother mechanical elements in which a rotating member is positionedadjacent a non-rotating member.

The optimal number, dimensions, geometries, relative placement, shapes,and/or configuration of the zones 20, 30, 40; radial holes 22, 32, 42;grooves 24, 34, 44; notches 15, and/or lands 16 will vary from oneembodiment of the bearing with axial variations 10 to the next, and aretherefore in no way limiting to the scope thereof. The various elementsof an apparatus using at least one feature of the present disclosure maybe formed of any material that is suitable for the application for whichthe apparatus is used. Such materials include but are not limited tometals and their metal alloys, polymeric materials, and/or combinationsthereof.

Although the specific embodiments pictured and described herein pertainto bearings having two or three radial holes 22, 32, 42 and two or threegrooves 24, 34, 44 evenly spaced about the circumference of the bearingwith axial variations 10, the bearing with axial variations 10 may beconfigured with other orientations and/or with different quantities ofthe various elements having different shapes and/or orientations,equally or unequally spaced from other elements within a given zone 20,30, 40 or from elements in a different zone 20, 30, 40. Furthermore, theradial holes 22, 32, 42 may be applied to structures other thanbearings, as described above. Accordingly, the scope of the presentdisclosure is in no way limited by the specific shape, configuration,and/or dimensions of the above elements, and/or the relative quantitiesand/or positions thereof.

Having described the preferred embodiments, other features, advantages,and/or efficiencies of the present disclosure will undoubtedly occur tothose versed in the art, as will numerous modifications and alterationsof the disclosed embodiments and methods, all of which may be achievedwithout departing from the spirit and scope of the present disclosure asdisclosed and claimed herein. Furthermore, variations and modificationsof the foregoing are within the scope of the bearing with axialvariations 10. It is understood that the scope of the bearing with axialvariations 10 as disclosed herein extends to all alternativecombinations of one or more of the individual features mentioned orevident from the text and/or drawings. All of these differentcombinations constitute various alternative aspects of the bearing withaxial variations 10. The embodiments described herein explain the bestmodes known for practicing the bearing with axial variations and willenable others skilled in the art to utilize the same. The claims are tobe construed to include alternative embodiments to the extent permittedby the prior art.

It should be noted that the present disclosure is not limited to thespecific embodiments pictured and described herein, but are intended toapply to all similar apparatuses for evenly accommodating different loadrequirements in a single apparatus. Modifications and alterations fromthe described embodiments will occur to those skilled in the art withoutdeparture from the spirit and scope of the present disclosure.

A first illustrative embodiment of a countershaft 100 according to thepresent disclosure is shown in FIGS. 8A-8E. The first illustrativeembodiment of a countershaft 100 may include a first bearing zone 120and a second bearing zone 130 separated by a spacer 112. The two bearingzones 120, 130 may be integrally formed with one another and/or thespacer 112, or the two bearing zones 120, 130 and/or spacer 112 may beseparately formed and later engaged with one another. For brevity,illustrative features of one of the bearing zones 120, 130 will bedescribed in detail, with the understanding that those features may beapplied to other bearing zones 120, 130 without limitation. Furthermore,although the embodiment shown in FIGS. 8A-8E includes two discretebearing zones 120, 130, in other embodiments of the countershaft 100additional bearing zones 120, 130 and/or spacers 112 may be includedwithout limitation.

The first hearing zone 120 may be configured with a land 116 having agroove 124 and taper 126 formed therein. The land 116 may be on theoutside diameter of the countershaft 100 in a manner similar to thatpreviously described above for the illustrative embodiments of a hearingwith axial variations 10 shown in FIGS. 5-7. It is contemplated thatcountershafts 100 configured with features according to the presentdisclosure may be especially useful in applications wherein thecountershaft 100 is stationary (or relatively stationary) and a largermember is positioned adjacent the outside diameter of the countershaft100, wherein the larger member may rotate with respect to thecountershaft 100. However, the specific application of the countershaft100 and/or configuration with respect to rotating and/or non-rotatingmembers in no way limits the scope of the present disclosure.

The embodiment of a countershaft 100 shown in FIGS. 8A-8E may includetwo bearing zones 120, 130 with at least one groove 124, 134 in eachrespective bearing zone 120, 130 positioned on the exterior of thecountershaft 100. The illustrative embodiment may be configured with anaxial channel 114 of a constant or varying profile along thelongitudinal length of the countershaft 100, as best shown in FIG. 8C.Additionally, the exterior of the countershaft 100 may have a constantor varying profile along its length. The various features in any groove124, 134, 144; taper 126, 136, 146; and/or land 116 may be anypreviously described for any embodiments of a bearing with axialvariations 10 without limitation. It is contemplated that lubricant maybe supplied to one or more radial holes 122, 132, 142 via a lubricantsupply source (not shown), such as a supply of pressurized lubricant.However, the specific method and/or apparatus used to supply lubricantto any radial hole 122, 132, 142 of any embodiment of the countershaft100 in no way limits the scope of the present disclosure.

One or more radial holes 122, 132 may be configured to be in fluidcommunication with both the axial channel 114 and any respective grooves124, 134, within the respective bearing zone 120, 130. An axial,cross-sectional view of the first illustrative embodiment of acountershaft 100 is shown in FIG. 8C, and a radial, cross-sectional viewat the first bearing zone 120 is shown in FIG. 8D and at the secondbearing zone 130 in FIG. 8E. In the first illustrative embodiment, boththe first and second bearing zones 120, 130 may include three radialholes 122, 132 offset from one another by more than 90 degrees but lessthan 180 degrees. However, other numbers, geometries, and/or overallconfigurations of the bearing zones 120, 130, radial holes 122, 132,grooves 124, 134 and/or lands 116 may be used without departing from thespirit and scope of the countershaft 100 as disclosed and claimedherein. The radial holes 122 in the first zone 120 may be rotationallyoffset from those in the second zone 130, as previously described forthe various embodiments of the bearing with axial variations 10.

A side view of a second embodiment of a countershaft 100 is shown inFIG. 9A. The second embodiment of a countershaft 100 may be formed withone or more radial holes 122, 132 may be configured to be in fluidcommunication with both an axial channel 114 formed along thelongitudinal axis of the countershaft 100 and any respective grooves124, 134, within the respective bearing zone 120, 130 as previouslydescribed for the embodiment pictured in FIGS. 8A-8E. The radial holes122 in the first bearing zone 120 may be radially offset from the radialholes 132 in the second zone 130 also as previously described for theembodiment pictured in FIGS. 8A-8E. One or more radial holes 122, 132may be configured to be in fluid communication with both the axialchannel 114 and any respective grooves 124, 134, within the respectivebearing zone 120, 130.

As is evident from a comparison between FIGS. 8A and 9A, the taper 126,136 for the embodiment shown in FIGS. 9A-9C may be circumferentiallyshorter than the taper 126, 136 for the embodiment shown in FIGS. 8A-8E.However, as previously described for the various embodiments of abearing with axial variations 10, the specific number, configuration,and/or characteristics of the grooves 124, 134 are in no way limiting tothe scope of the present disclosure. Accordingly, other numbers,geometries, and/or overall configurations of the bearing zones 120, 130,radial holes 122, 132, grooves 124, 134; tapers 126, 136, 146 and/orlands 116 may be used without departing from the spirit and scope of thecountershaft 100 as disclosed and claimed herein.

The number, configuration, dimensions, geometries, and/or relativelocations of the bearing zones 120, 130; spacers 112; radial holes 122,132; grooves 124, 134; notches 15, and/or lands 116 will vary from oneembodiment of the countershaft 100 to the next, as will the optimalconfiguration thereof. Accordingly, the countershaft 100 as disclosedand claimed herein is in no way limited by the specific constraints ofthose elements. In addition to optimizing the rotational offset betweenbearing zones 120, 130, the number of features (e.g., radial holes 122,132; grooves 124, 134; grooves, tapers 126, 136, profiles; etc.); and/orlands 116 and the configuration thereof may be optimized for specificoperational requirements and/or constraints.

The countershaft 100 as disclosed and claimed herein may extend to anycountershaft 100 with a fixed profile, including but not limited toplain cylindrical countershafts, elliptical countershafts, taper landcountershafts, pressure dam countershafts, tilting pad countershafts,and offset half countershafts. Furthermore, the present disclosure maybe applied to any countershaft or other mechanical elements in which arotating member is positioned adjacent a non-rotating member.

The optimal number, dimensions, geometries, relative placement, shapes,and/or configuration of the bearing zones 120, 130; radial holes 122,132; grooves 124, 134; notches 15, and/or lands 116 will vary from oneembodiment of the countershaft 100 to the next, and are therefore in noway limiting to the scope thereof. The various elements of an apparatususing at least one feature of the present disclosure may be formed ofany material that is suitable for the application for which theapparatus is used. Such materials include but are not limited to metalsand their metal alloys, polymeric materials, and/or combinationsthereof.

Although the specific embodiments pictured and described herein pertainto countershafts 10 having two bearing zones 120, 130; two or threeradial holes 122, 132; and two or three grooves 124, 134 evenly spacedabout the circumference of the countershaft 100, the countershaft 100may be configured with other orientations and/or with differentquantities of the various elements having different shapes and/ororientations. Accordingly, the scope of the present disclosure is in noway limited by the specific shape, configuration, and/or dimensions ofthe above elements, and/or the relative quantities and/or positionsthereof.

Having described the preferred embodiments, other features, advantages,and/or efficiencies of the present disclosure will undoubtedly occur tothose versed in the art, as will numerous modifications and alterationsof the disclosed embodiments and methods, all of which may be achievedwithout departing from the spirit and scope of the present disclosure asdisclosed and claimed herein. Furthermore, variations and modificationsof the foregoing are within the scope of the countershaft 100. It isunderstood that the scope of the countershaft as disclosed hereinextends to all alternative combinations of one or more of the individualfeatures mentioned or evident from the text and/or drawings. All ofthese different combinations constitute various alternative aspects ofthe countershaft. The embodiments described herein explain the bestmodes known for practicing the bearing with axial variations and willenable others skilled in the art to utilize the same. The claims are tobe construed to include alternative embodiments to the extent permittedby the prior art.

It should be noted that the present disclosure is not limited to thespecific embodiments pictured and described herein, but are intended toapply to all similar apparatuses for evenly accommodating different loadrequirements in a single apparatus. Modifications and alterations fromthe described embodiments will occur to those skilled in the art withoutdeparture from the spirit and scope of the present disclosure.

1. A countershaft comprising: a. an axial channel formed along thelongitudinal axis of said countershaft; b. a first bearing zone formedon an exterior surface of said countershaft, wherein said first bearingzone includes a groove and a taper positioned adjacent one another; c. asecond bearing zone formed on said exterior surface of saidcountershaft, wherein said second bearing zone includes a groove and ataper positioned adjacent one another, and wherein said groove in saidfirst zone and said groove in said second zone are rotationally offsetfrom one another; d. a first radial hole formed in said countershaft,wherein said first radial hole fluidly connects said axial channel tosaid groove in said first bearing zone; and, e. a second radial holeformed in said countershaft, wherein said second radial hole fluidlyconnects said axial channel to said groove in said second bearing zone.2. The countershaft according to claim 1 wherein said groove in saidfirst bearing zone further comprises a notch.
 3. The countershaftaccording to claim 2 wherein said groove in said second bearing zonefurther comprises a notch.
 4. The countershaft according to claim 1wherein said countershaft further comprises a second groove in saidfirst bearing zone and a third radial hole fluidly connecting said axialchannel to said second groove in said first bearing zone.
 5. Thecountershaft according to claim 4 wherein said countershaft furthercomprises a second groove in said second bearing zone and a fourthradial hole fluidly connecting said axial channel to said second groovein said second bearing zone.
 6. The countershaft according to claim 4wherein said countershaft further comprises a taper positioned adjacentsaid second groove in said first bearing zone.
 7. The countershaftaccording to claim 5 wherein said countershaft further comprises a taperpositioned adjacent said second groove in said second bearing zone. 8.The countershaft according to claim 7 wherein said countershaft furthercomprises an land positioned adjacent said tapers in said first bearingzone.
 9. The countershaft according to claim 8 wherein said countershaftfurther comprises an land positioned said tapers in said second bearingzone.
 10. The countershaft according to claim 8 wherein said land insaid first bearing zone is further defined as having no profile formedtherein.
 11. The countershaft according to claim 9 wherein said land insaid second bearing zone is further defined as having no profile formedtherein.
 12. A countershaft comprising: a. an axial channel formed alongthe longitudinal axis of said countershaft; b. a first bearing zoneformed on an exterior surface of said countershaft, wherein said firstbearing zone includes a groove, a taper positioned adjacent said groove,and an land positioned adjacent said taper, and wherein a radialdimension of said countershaft varies along the circumference thereofbetween said groove and an interface between said taper and said land;c. a second bearing zone formed on said exterior surface of saidcountershaft, wherein said second bearing zone includes a groove, ataper positioned adjacent said groove, and an land positioned adjacentsaid taper, wherein a radial dimension of said countershaft varies alongthe circumference thereof between said groove and an interface betweensaid taper and said land, and wherein said groove in said first zone andsaid groove in said second zone are rotationally offset from oneanother; d. a first radial hole formed in said countershaft, whereinsaid first radial hole fluidly connects said axial channel to saidgroove in said first bearing zone; and, e. a second radial hole formedin said countershaft, wherein said second radial hole fluidly connectssaid axial channel to said groove in said second bearing zone.
 13. Thecountershaft according to claim 12 further comprising: a. a secondgroove and a second taper positioned in said first bearing zone; and, b.a third radial hole formed in said countershaft, wherein said thirdradial hole fluidly connects said axial channel to said second groove insaid first bearing zone.
 14. The countershaft according to claim 13further comprising: a. a second groove and a second taper positioned insaid second bearing zone; and, b. a fourth radial hole formed in saidcountershaft, wherein said fourth radial hole fluidly connects saidaxial channel to said second groove in said second bearing zone.
 15. Thecountershaft according to claim 14 wherein said first and second groovesin said first bearing zone are further defined as being rotationallyoffset from one another by 180 degrees.
 16. The countershaft accordingto claim 15 wherein said first and second grooves in said second bearingzone are further defined as being rotationally offset from one anotherby 180 degrees.
 17. The countershaft according to claim 16 wherein saidfirst groove in said first bearing zone and said first groove in saidsecond bearing zone are further defined as being rotationally offsetfrom one another by an amount between 5 and 179 degrees.
 18. A method ofaccommodating a plurality of forces experienced by a countershaft, saidmethod comprising the steps of: a. forming a first bearing zone on anexterior surface of said countershaft, wherein said first bearing zoneincludes a groove and a taper positioned adjacent one another; b.forming a second bearing zone on an exterior surface of saidcountershaft, wherein said second bearing zone includes a groove and ataper positioned adjacent one another and wherein said groove in saidfirst zone and said groove in said second zone are rotationally offsetfrom one another; c. supplying a pressurized fluid to an axial channelformed along the longitudinal axis of said countershaft; d. allowingsaid pressurized fluid to migrate to said groove in said first bearingzone via a radial hole fluidly connecting said axial channel and saidgroove in said first bearing zone; e. allowing said pressurized fluid tomigrate to said groove in said second bearing zone via a second radialhole fluidly connecting said axial channel and said groove in saidsecond bearing zone; configuring a profile in said groove and said taperof said first zone to accommodate a first force experienced by saidcountershaft; and, g. configuring a profile in said groove and saidtaper of said second zone to accommodate a second force experienced bysaid countershaft, wherein said first and second forces are not equal ineither a direction or a magnitude.